CN113309833A - Engaged stepless speed change mechanism - Google Patents
Engaged stepless speed change mechanism Download PDFInfo
- Publication number
- CN113309833A CN113309833A CN202110695034.7A CN202110695034A CN113309833A CN 113309833 A CN113309833 A CN 113309833A CN 202110695034 A CN202110695034 A CN 202110695034A CN 113309833 A CN113309833 A CN 113309833A
- Authority
- CN
- China
- Prior art keywords
- bevel gear
- polygonal
- input
- housing
- curved
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 230000007246 mechanism Effects 0.000 title claims abstract description 37
- 230000008859 change Effects 0.000 title claims abstract description 28
- 230000005540 biological transmission Effects 0.000 claims abstract description 31
- 230000013011 mating Effects 0.000 description 25
- 238000010586 diagram Methods 0.000 description 8
- 238000012423 maintenance Methods 0.000 description 6
- 239000002131 composite material Substances 0.000 description 2
- 230000007547 defect Effects 0.000 description 2
- 230000009347 mechanical transmission Effects 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000007689 inspection Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000005272 metallurgy Methods 0.000 description 1
- 239000003208 petroleum Substances 0.000 description 1
- 239000000126 substance Substances 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/42—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion with gears having teeth formed or arranged for obtaining multiple gear ratios, e.g. nearly infinitely variable
- F16H3/423—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion with gears having teeth formed or arranged for obtaining multiple gear ratios, e.g. nearly infinitely variable the teeth being arranged on a surface of generally conical shape
Abstract
The invention relates to an alternating engagement stepless speed change mechanism, and belongs to the field of stepless speed change. The input end involute bevel gear is arranged outside the polygonal input shaft and is respectively in threaded connection with the input end involute bevel gear and the adjusting screw. The power transmission efficiency is high, and the transmission ratio range is wide.
Description
Technical Field
The invention relates to the technical field of stepless speed change, in particular to an engagement stepless speed change mechanism.
Background
The stepless speed change principle is widely applied in production and life, for example, except that the automobile stepless speed change box is relatively recognized by people, the stepless speed change principle is also widely applied to the fields of light industry, machine tools, metallurgy, mines, petroleum, chemical industry and the like.
However, the automobile continuously variable transmission requires the characteristics of economy, reliability, small volume, light weight and the like because of the use scene of the automobile continuously variable transmission.
In spite of the fact that the most representative CVT is good in the existing automobile continuously variable transmission, some defects are highlighted in the practical use process, for example, the CVT utilizes friction force to transmit power, the transmission is easy to slip when transmitting power, the service life is short, the maintenance is high in the middle period, and the problem that the CVT cannot bear large torque is solved.
Disclosure of Invention
Aiming at the defects in the prior art, the invention provides the alternating engagement stepless speed change mechanism which has the advantages of high power transmission efficiency, high reliability, large transmission ratio range, small number of used parts and low later maintenance cost.
In order to achieve the above purpose, the solution adopted by the invention is as follows:
a cross-meshing stepless speed change mechanism comprises a cross-meshing stepless speed change mechanism main body, wherein the cross-meshing stepless speed change mechanism main body comprises a polygonal input shaft, a polygonal output shaft, an input end gradually-opening bevel gear, an output end gradually-opening bevel gear, an input end adjusting bush, an output end adjusting bush, an adjusting screw rod, an upper matching bevel gear, a lower matching bevel gear, a middle matching bevel gear, a central support cover, an upper equal-division curved-profile fluted disc and a lower equal-division curved-profile fluted disc, the polygonal input shaft and the polygonal output shaft are symmetrically and rotatably arranged at two ends of the center of the central support cover, the upper matching bevel gear and the lower matching bevel gear are symmetrically and rotatably arranged at the upper end and the lower end of the central support cover, the central matching bevel gear is rotatably arranged at the first end and is fixedly connected with the upper matching bevel gear and the lower matching bevel gear respectively, the upper equal-division curved fluted disc and the lower equal-division curved fluted disc have the same structure and are uniformly divided into a plurality of fan-shaped areas, curved toothed racks are arranged at intervals in the plurality of fan-shaped areas, the upper division curved fluted disc and the lower division curved fluted disc are symmetrically arranged at the upper end and the lower end of the central support cover in a staggered way and are respectively meshed with the upper matching bevel gear and the lower matching bevel gear, the adjusting screw is rotatably arranged at the second end, the input end involute bevel gear comprises an input end involute bevel gear main body and a first connecting part connected with the input end involute bevel gear main body, the input end involute bevel gear main body and the first connecting part are both sleeved outside the polygonal input shaft, one end of the input end adjusting bushing is sleeved outside the first connecting part and is rotatably connected with the first connecting part, the other end of the input end adjusting bushing is in threaded connection with the adjusting screw, the output end involute bevel gear comprises an output end involute bevel gear main body and a second connecting part connected with the output end involute bevel gear main body, the output end involute bevel gear main body and the second connecting portion are sleeved outside the polygonal output shaft, one end of the output end adjusting bushing is sleeved outside the second connecting portion and is connected with the second connecting portion in a rotating mode, and the other end of the output end adjusting bushing is connected with the adjusting screw in a threaded mode.
Further, in a preferred embodiment of the present invention, the polygonal input shaft may be a triangular input shaft, a quadrangular input shaft, a pentagonal input shaft or a hexagonal input shaft.
Further, in a preferred embodiment of the present invention, the polygonal input shaft is a hexagonal input shaft.
Further, in a preferred embodiment of the present invention, the polygonal output shaft may be a triangular output shaft, a quadrangular output shaft, a pentagonal output shaft or a hexagonal output shaft.
Further, in a preferred embodiment of the present invention, the polygonal output shaft is a hexagonal output shaft.
Further, in a preferred embodiment of the present invention, the meshing stepless speed change mechanism further includes a housing, the housing is covered outside the meshing stepless speed change mechanism main body, the polygonal input shaft and the polygonal output shaft both extend to the outside of the housing and are rotatably connected to the housing, and one end of the adjusting screw extends to the outside of the housing and is rotatably connected to the housing.
Further, in a preferred embodiment of the present invention, the housing includes a first housing and a second housing, and the first housing and the second housing are detachably connected.
The invention provides a stepless speed change mechanism with two involute conical gears changed in meshing, which has the beneficial effects that: when the upper equal-division curved-profile fluted disc, the lower equal-division curved-profile fluted disc, the input end involute bevel gear and the output end involute bevel gear are meshed alternately in a timing mode, the relative positions of the input end involute bevel gear on the input shaft and the output end involute bevel gear on the output shaft are changed, the mechanical transmission mechanism capable of continuously changing the transmission ratio is achieved, the transmission efficiency of the mechanism for transmitting power by means of racks and gears is high, the reliability is high, the transmission ratio range is large, the number of used parts is small, the later maintenance cost is low, and the like.
Drawings
In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings needed to be used in the embodiments will be briefly described below, it should be understood that the following drawings only illustrate some embodiments of the present invention and therefore should not be considered as limiting the scope, and for those skilled in the art, other related drawings can be obtained according to the drawings without inventive efforts.
Fig. 1 is a schematic structural diagram of a main body of an intermeshing continuously variable transmission provided in an embodiment of the present invention at a first viewing angle;
FIG. 2 is a schematic structural diagram of a main body of an intermeshing continuously variable transmission mechanism according to an embodiment of the invention from a second perspective;
FIG. 3 is a schematic structural diagram of a main body of an intermeshing continuously variable transmission mechanism according to an embodiment of the invention from a third perspective;
FIG. 4 is a schematic structural diagram of a center support cover according to an embodiment of the present invention;
FIG. 5 is a schematic structural diagram of an upper-graduation curved-profile fluted disc according to an embodiment of the present invention;
FIG. 6 is a schematic view of the connection of an adjusting screw according to an embodiment of the present invention;
FIG. 7 is a schematic structural diagram of an input end involute bevel gear according to an embodiment of the invention;
FIG. 8 is a schematic structural diagram of an output end involute bevel gear according to an embodiment of the invention;
fig. 9 is a schematic structural diagram of an intermeshing stepless speed change mechanism according to an embodiment of the invention.
Icon: 100-meshing stepless speed change mechanism; 110-meshing stepless speed change mechanism body; 120-a housing; 121-a first housing; 122-a second housing; 210-polygonal input shaft; 220-polygonal output shaft; 310-input involute bevel gear; 311-input involute bevel gear body; 312 — a first connection; 320-output end involute bevel gear; 321-an output end involute bevel gear body; 322-a second connecting portion; 410-input end adjustment bushing; 420-output end adjustment bushing; 500-adjusting the screw; 610-upper mating bevel gear; 620-lower mating bevel gear; 630-an intermediate mating bevel gear; 700-center support shield; 710-a third terminal; 720-fourth end; 730-first end; 740-a second end; 810-an upper equal-division curved profile fluted disc; 820-lower equal-division curved profile fluted disc; 830-sector area; 840-curved profile rack.
Detailed Description
To make the objects, technical solutions and advantages of the embodiments of the present invention clearer, the technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are some embodiments of the present invention, but not all embodiments. The components of embodiments of the present invention generally described and illustrated in the figures herein may be arranged and designed in a wide variety of different configurations.
Thus, the following detailed description of the embodiments of the present invention, presented in the figures, is not intended to limit the scope of the invention, as claimed, but is merely representative of selected embodiments of the invention. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
It should be noted that: like reference numbers and letters refer to like items in the following figures, and thus, once an item is defined in one figure, it need not be further defined and explained in subsequent figures.
In the description of the present invention, it should be noted that the terms "upper", "lower", "inside", "outside", and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings or orientations or positional relationships conventionally put in use of products of the present invention, and are only for convenience of description and simplification of description, but do not indicate or imply that the devices or elements referred to must have specific orientations, be constructed in specific orientations, and be operated, and thus, should not be construed as limiting the present invention. Furthermore, the terms "first," "second," and the like are used solely to distinguish one from another and are not to be construed as indicating or implying relative importance.
Furthermore, the terms "horizontal", "vertical" and the like do not imply that the components are required to be absolutely horizontal or pendant, but rather may be slightly inclined. For example, "horizontal" merely means that the direction is more horizontal than "vertical" and does not mean that the structure must be perfectly horizontal, but may be slightly inclined.
In the description of the present invention, it should also be noted that, unless otherwise explicitly specified or limited, the terms "disposed," "connected," and "connected" are to be construed broadly, e.g., as meaning fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art.
Examples
Referring to fig. 1, the present embodiment provides an intermeshing stepless speed change mechanism 100, which includes an intermeshing stepless speed change mechanism body 110, wherein the intermeshing stepless speed change mechanism body 110 includes a polygonal input shaft 210, a polygonal output shaft 220, an input end involute bevel gear 310, an output end involute bevel gear 320, an input end adjusting bushing 410, an output end adjusting bushing 420, an adjusting screw 500, an upper mating bevel gear 610, a lower mating bevel gear 620, a middle mating bevel gear 630, a central support cover 700, an upper equal-pitch curved-profile fluted disc 810, and a lower equal-pitch curved-profile fluted disc 820.
Referring to fig. 1, 2, 3 and 4, the polygonal input shaft 210 and the polygonal output shaft 220 are symmetrically and rotatably disposed at two ends of the center support cover 700, and in the present invention, the polygonal input shaft 210 and the polygonal output shaft 220 are rotatably disposed at two ends of the center support cover 700 through bearings. Specifically, the center support housing 700 includes a third end 710 and a fourth end 720, which are opposite to each other, and the polygonal input shaft 210 is rotatably disposed at the third end 710 and the polygonal output shaft 220 is rotatably disposed at the fourth end 720.
The upper and lower engaging bevel gears 610 and 620 are symmetrically and rotatably disposed at upper and lower ends of the center support cap 700, that is, in the present invention, the upper and lower engaging bevel gears 610 and 620 are symmetrically disposed at upper and lower ends of the center support cap 700 and are both rotatably disposed at upper and lower ends of the center support cap 700. The center support cap 700 includes a first end 730 and a second end 740 disposed opposite to each other, and the intermediate mating bevel gear 630 is rotatably disposed at the first end 730 and engaged with the upper mating bevel gear 610 and the lower mating bevel gear 620, respectively, that is, the upper mating bevel gear 610 can rotate to drive the intermediate mating bevel gear 630 to rotate and then drive the lower mating bevel gear 620 to rotate, or the lower mating bevel gear 620 can rotate to drive the intermediate mating bevel gear 630 to rotate and then drive the upper mating bevel gear 610 to rotate.
Referring to fig. 5, the upper and lower equally-divided curved- profile toothed discs 810 and 820 have the same structure and are divided into a plurality of fan-shaped regions 830, that is, the upper equally-divided curved-profile toothed disc 810 is divided into a plurality of fan-shaped regions 830, the lower equally-divided curved-profile toothed disc 820 is divided into a plurality of fan-shaped regions 830, the plurality of fan-shaped regions 830 are provided with curved-profile racks 840 at intervals, that is, two adjacent curved-profile racks 840 in one fan-shaped region 830 are not provided. The number of the 12-equal-division curved-profile fluted discs adopted in the invention is not limited, and can be other numbers, and the number of the equal-division curved-profile fluted discs in practical application is set according to the size of the mechanism.
Referring to fig. 1, 2, 3, 4, 5 and 6, the upper and lower equi-indexing curved-profile toothed discs 810 and 820 are symmetrically disposed at the upper and lower ends of the central support cover 700 in a staggered manner and are fixedly connected to the upper and lower mating bevel gears 610 and 620, respectively, that is, first, the upper and lower equi-indexing curved- profile toothed discs 810 and 820 are symmetrically disposed at the upper and lower ends of the central support cover 700, meanwhile, the upper equal-division curved-profile fluted disc 810 and the lower equal-division curved-profile fluted disc 820 are arranged in a staggered manner, that is, the fan-shaped region 830 where the upper equal-division curved-profile fluted disc 810 is provided with the curved-profile toothed rack 840 and the fan-shaped region 830 where the lower equal-division curved-profile fluted disc 820 is provided with the curved-profile toothed rack 840 are arranged in a staggered manner, that is, the fan-shaped region 830 where the upper equal-division curved-profile fluted disc 810 is provided with the curved-profile toothed rack 840 corresponds to the fan-shaped region 830 where the lower equal-division curved-profile fluted disc 820 is not provided with the curved-profile toothed rack 840. Meanwhile, the upper equal-division curved-profile fluted disc 810 is fixedly connected with the upper matching bevel gear 610, and the lower equal-division curved-profile fluted disc 820 is fixedly connected with the lower matching bevel gear 620, that is, the upper equal-division curved-profile fluted disc 810 rotates to drive the upper matching bevel gear 610 to rotate, and the lower equal-division curved-profile fluted disc 820 rotates to drive the lower matching bevel gear 620 to rotate.
Referring to fig. 1, 7 and 8, the adjusting screw 500 is rotatably disposed at the second end 740, the input-end involute bevel gear 310 includes an input-end involute bevel gear main body 311 and a first connecting portion 312 connected to the input-end involute bevel gear main body 311, the input-end involute bevel gear main body 311 and the first connecting portion 312 are both sleeved outside the polygonal input shaft 210, so as to drive the input-end involute bevel gear 310 to rotate when the polygonal input shaft 210 rotates, one end of the input-end adjusting bushing 410 is sleeved outside the first connecting portion 312 and rotatably connected to the first connecting portion 312, and the other end is in threaded connection with the adjusting screw 500, so as to drive the input-end involute bevel gear 310 to rotate left and right when the input-end adjusting bushing 410 moves left and right.
The output end involute bevel gear 320 comprises an output end involute bevel gear main body 321 and a second connecting part 322 connected with the output end involute bevel gear main body 321, the output end involute bevel gear main body 321 and the second connecting part 322 are both sleeved outside the polygonal output shaft 220, the purpose is to drive the output end involute bevel gear 320 to rotate when the polygonal output shaft 220 rotates, one end of an output end adjusting bushing 420 is sleeved outside the second connecting part 322 and is rotatably connected with the second connecting part 322, the other end of the output end adjusting bushing is in threaded connection with the adjusting screw 500, and the purpose is to drive the output end involute bevel gear 320 to rotate left and right when the output end adjusting bushing 420 moves left and right.
The principle of the alternating engagement continuously variable transmission mechanism 100 is as follows: when the bevel gear type wheel hub is used, the polygonal input shaft 210 is connected with an engine (not shown), the adjusting screw 500 is connected with a motor (not shown), the polygonal input shaft 210 is driven to rotate by the engine, the polygonal input shaft 210 rotates to drive the input end involute bevel gear 310 to rotate, when the input end involute bevel gear 310 is meshed with the lower equal-division involute bevel gear 820, the lower equal-division involute bevel gear 820 drives the lower matching bevel gear 620 and the output end involute bevel gear 320 to rotate, and the output end involute bevel gear 320 transmits power to wheels through the polygonal output shaft 220; the rotation of the lower mating bevel gear 620 can drive the middle mating bevel gear 630 to rotate and further drive the upper mating bevel gear 610 to rotate, the upper mating bevel gear 610 drives the upper equal-division curved-profile fluted disc 810 to rotate, so that the upper equal-division curved-profile fluted disc 810 and the lower equal-division curved-profile fluted disc 820 rotate in the same angular speed in the opposite direction, the upper equal-division curved-profile fluted disc 810 and the input-end involute bevel gear 310 start to mesh before the input-end involute bevel gear 310 and the lower equal-division curved-profile fluted disc 820 are disengaged, then the upper equal-division curved-profile fluted disc 810 rotates to drive the output-end involute bevel gear 320 and the upper mating bevel gear 610 to rotate, and the output-end involute bevel gear 320 transmits power to the wheel through the polygonal output shaft 220; the upper mating bevel gear 610 drives the middle mating bevel gear 630 to rotate and further drives the lower mating bevel gear 620 to rotate, and the lower mating bevel gear 620 drives the lower equi-division curved-profile fluted disc 820 to rotate, so that the lower equi-division curved-profile fluted disc 820 and the upper equi-division curved-profile fluted disc 810 rotate in the same angular speed in the opposite direction, and the lower equi-division curved-profile fluted disc 820 and the input involute tapered gear 310 start to mesh before the input involute tapered gear 310 and the upper equi-division curved-profile fluted disc 810 are disengaged. This causes the relationship of input involute bevel gear 310 meshing with upper and lower equal-index curved toothed discs 810 and 820 to be alternately cycled. The same alternating meshing relationship is alternately cycled between upper equi-indexed curved toothed disc 810, lower equi-indexed curved toothed disc 820, and output involute bevel gear 320 such that power is continuously transmitted from input involute bevel gear 310 to output involute bevel gear 320. In the process of transmitting power from the input end involute bevel gear 310 to the output end involute bevel gear 320, the motor drives the adjusting screw 500 to rotate, when the adjusting screw 500 rotates, the input end adjusting bushing 410 and the output end adjusting bushing 420 which can be controlled to move, the input end adjusting bushing 410 drives the input end involute bevel gear 310, and the output end adjusting bushing 420 drives the output end involute bevel gear 320 to move on the polygonal input shaft 210 and the polygonal output shaft 220 respectively. Since the angular velocities of the lower equi-division curved-profile toothed disc 820 and the upper equi-division curved-profile toothed disc 810 are the same, and the linear velocity is larger as the angular velocity is constant and is farther from the center, when one of the input-end involute conical gear 310 and the output-end involute conical gear 320 moves to be close to the central support cover 700 and the other one is far from the central support cover 700, the transmission ratio between the polygonal input shaft 210 and the polygonal output shaft 220 is larger, since the curved-profile racks of the upper equi-division curved-profile toothed disc 810 and the lower equi-division curved-profile toothed disc 820 are distributed outwards from the center, the input-end involute conical gear 310 and the output-end involute conical gear 320 move outwards from the center or outwards to the center without being affected, and finally, the continuously variable transmission ratio of power input and output is realized, and the purpose of stepless speed change is achieved. Based on monomeric composite mechanism, through increasing involute bevel gear and increasing graduation curved profile fluted disc with specific structure combination collocation, the performance that obtains is more stable, bears the moment bigger, the wider composite speed change mechanism in application field, the device relies on rack and pinion transmission power's transmission efficiency height, the reliability is high, the drive ratio scope is big, used part is small in quantity, later maintenance cost low grade.
Further, the polygonal input shaft 210 may be a polygonal input shaft, a quadrangular input shaft, a pentagonal input shaft, or a hexagonal input shaft, but is not limited thereto, and may also be an octagonal input shaft, etc., and a hexagonal input shaft is used in the present invention.
Further, the polygonal output shaft 220 may be a triangular output shaft, a quadrangular output shaft, a pentagonal output shaft, or a hexagonal output shaft, but is not limited thereto, and may also be an octagonal output shaft, and the hexagonal output shaft is used in the present invention.
Referring to fig. 9, further, the intermeshing continuously variable transmission 100 further includes a housing 120, the housing 120 is covered outside the intermeshing continuously variable transmission main body 110 for protecting the intermeshing continuously variable transmission main body 110, wherein the polygonal input shaft 210 and the polygonal output shaft 220 both extend outside the housing 120 and are rotatably connected to the housing 120, the polygonal input shaft 210 extends outside the housing 120 for connection to an engine, the polygonal output shaft 220 extends outside the housing 120 for connection to a wheel, one end of the adjusting screw 500 extends outside the housing 120 and is rotatably connected to the housing 120, and one end of the adjusting screw 500 extends outside the housing 120 for connection to a motor.
Further, the housing 120 includes a first housing 121 and a second housing 122, and the first housing 121 and the second housing 122 are detachably connected to facilitate the detachment, inspection, maintenance, and maintenance of the meshing continuously variable transmission main body 110.
In summary, the continuously variable transmission mechanism with two involute bevel gears changed in meshing manner mainly changes the relative positions of the involute bevel gears at the input end and the output end on the input shaft and the output shaft by the involute bevel gears at the input end when the upper and lower equal-division curved-profile fluted discs are meshed with the involute bevel gears at the input end and the output end in a timing alternate manner, so that the mechanical transmission mechanism with continuously variable transmission ratio is realized.
The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention, and various modifications and changes may be made by those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (7)
1. A cross-meshing stepless speed change mechanism is characterized by comprising a cross-meshing stepless speed change mechanism main body, wherein the cross-meshing stepless speed change mechanism main body comprises a polygonal input shaft, a polygonal output shaft, an input end involute bevel gear, an output end involute bevel gear, an input end adjusting bushing, an output end adjusting bushing, an adjusting screw, an upper matching bevel gear, a lower matching bevel gear, a middle matching bevel gear, a central support cover, an upper-dividing curved-profile fluted disc and a lower-dividing curved-profile fluted disc, the polygonal input shaft and the polygonal output shaft are symmetrically and rotatably arranged at two ends of the center of the central support cover, the upper matching bevel gear and the lower matching bevel gear are symmetrically and rotatably arranged at the upper end and the lower end of the central support cover, the central support cover comprises a first end and a second end which are oppositely arranged, the middle matching bevel gear is rotatably arranged at the first end and is respectively meshed with the upper matching bevel gear and the lower matching bevel gear, the upper equal-division curved-profile fluted disc and the lower equal-division curved-profile fluted disc are identical in structure and are uniformly divided into a plurality of sector areas, curved-profile racks are arranged in the sector areas at intervals, the upper equal-division curved-profile fluted disc and the lower equal-division curved-profile fluted disc are symmetrically, staggeredly and rotatably arranged at the upper end and the lower end of the central support cover and are fixedly connected with the upper matching bevel gear and the lower matching bevel gear respectively, the adjusting screw is rotatably arranged at the second end, the input-end involute bevel gear comprises an input-end involute bevel gear main body and a first connecting part connected with the input-end involute bevel gear main body, the input-end involute bevel gear main body and the first connecting part are both sleeved outside the polygonal input shaft, and one end of the input-end adjusting bushing is sleeved outside the first connecting part and is rotatably connected with the first connecting part, the other end of the output end involute bevel gear is in threaded connection with the adjusting screw, the output end involute bevel gear comprises an output end involute bevel gear body and a second connecting portion connected with the output end involute bevel gear body, the output end involute bevel gear body and the second connecting portion are all sleeved outside the polygonal output shaft, one end of the output end adjusting bushing is sleeved outside the second connecting portion and is in rotating connection with the second connecting portion, and the other end of the output end adjusting bushing is in threaded connection with the adjusting screw.
2. An intermeshing continuously variable transmission mechanism as claimed in claim 1 wherein the polygonal input shaft is a trilateral input shaft, a quadrilateral input shaft, a pentagonal input shaft or a hexagonal input shaft.
3. The intermeshing continuously variable transmission mechanism of claim 2 wherein the polygonal input shaft is a hexagonal input shaft.
4. An intermeshing stepless speed change mechanism as claimed in claim 2, wherein the polygonal output shaft may be a triangular output shaft, a quadrilateral output shaft, a pentagonal output shaft or a hexagonal output shaft.
5. The intermeshing continuously variable transmission mechanism of claim 4 wherein the polygonal output shaft is a hexagonal output shaft.
6. The intermeshing continuously variable transmission mechanism as claimed in claim 1, further comprising a housing, wherein the housing is covered outside the main body of the intermeshing continuously variable transmission mechanism, the polygonal input shaft and the polygonal output shaft both extend out of the housing and are rotatably connected with the housing, and one end of the adjusting screw extends out of the housing and is rotatably connected with the housing.
7. The intermeshing continuously variable transmission mechanism of claim 6 wherein the housing comprises a first housing and a second housing, the first housing and the second housing being removably connected.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110695034.7A CN113309833A (en) | 2021-06-22 | 2021-06-22 | Engaged stepless speed change mechanism |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110695034.7A CN113309833A (en) | 2021-06-22 | 2021-06-22 | Engaged stepless speed change mechanism |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN113309833A true CN113309833A (en) | 2021-08-27 |
Family
ID=77379839
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202110695034.7A Pending CN113309833A (en) | 2021-06-22 | 2021-06-22 | Engaged stepless speed change mechanism |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN113309833A (en) |
Citations (18)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR373411A (en) * | 1907-01-09 | 1907-05-15 | Francois Jacques Merle | Variable speed transmission by friction wheels with pressure disc and spacer rollers |
| GB142644A (en) * | 1919-04-22 | 1920-05-13 | Harold Cornelius Reading | Improvements relating to friction gearing |
| US1431049A (en) * | 1921-02-28 | 1922-10-03 | Frank E Schoonmaker | Transmission mechanism |
| US1883749A (en) * | 1931-01-14 | 1932-10-18 | Edward K Standish | Variable speed transmission |
| US2057482A (en) * | 1933-02-03 | 1936-10-13 | Erban Patents Corp | Friction gear |
| FR1147943A (en) * | 1955-10-12 | 1957-12-02 | Speed variator | |
| GB1148886A (en) * | 1965-09-10 | 1969-04-16 | Nat Res Dev | Variable ratio transmission unit |
| GB1153572A (en) * | 1965-07-16 | 1969-05-29 | Nat Res Dev | Variable Ratio Transmission Unit |
| US4304154A (en) * | 1978-09-05 | 1981-12-08 | Gkn Group Services Limited | Variable ratio transmission mechanism |
| US4819494A (en) * | 1987-04-01 | 1989-04-11 | Giuliani Robert L | Continuously variable transmission |
| DE4012060A1 (en) * | 1989-04-19 | 1990-10-25 | Takashi Takahashi | CONTINUOUS VARIABLE GEARBOX |
| FR2675875A1 (en) * | 1991-01-18 | 1992-10-30 | Ching Shiang Huang | Variable-speed transmission mechanism |
| WO1992022759A1 (en) * | 1991-06-13 | 1992-12-23 | Dong Hwi Lee | Rotary to stepless motion converter |
| US5472388A (en) * | 1991-12-19 | 1995-12-05 | Lee; Dong H. | Rotary to stepless motion converter |
| FR2776736A1 (en) * | 1998-03-24 | 1999-10-01 | Thomson Csf | Variable speed friction drive for alternator driven by aircraft engine turbine |
| RU2004107886A (en) * | 2004-03-18 | 2005-10-10 | Ким Дмитриевич Макин (RU) | DRIVE DRIVE VARIATOR |
| WO2021024177A1 (en) * | 2019-08-05 | 2021-02-11 | Johannes Jacobus Naude | Continuously variable transmission with variable disk traction drive |
| CN212584206U (en) * | 2020-06-19 | 2021-02-23 | 李哲南 | Stepless speed variator |
-
2021
- 2021-06-22 CN CN202110695034.7A patent/CN113309833A/en active Pending
Patent Citations (19)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR373411A (en) * | 1907-01-09 | 1907-05-15 | Francois Jacques Merle | Variable speed transmission by friction wheels with pressure disc and spacer rollers |
| GB142644A (en) * | 1919-04-22 | 1920-05-13 | Harold Cornelius Reading | Improvements relating to friction gearing |
| US1431049A (en) * | 1921-02-28 | 1922-10-03 | Frank E Schoonmaker | Transmission mechanism |
| US1883749A (en) * | 1931-01-14 | 1932-10-18 | Edward K Standish | Variable speed transmission |
| US2057482A (en) * | 1933-02-03 | 1936-10-13 | Erban Patents Corp | Friction gear |
| FR1147943A (en) * | 1955-10-12 | 1957-12-02 | Speed variator | |
| GB1153572A (en) * | 1965-07-16 | 1969-05-29 | Nat Res Dev | Variable Ratio Transmission Unit |
| GB1148886A (en) * | 1965-09-10 | 1969-04-16 | Nat Res Dev | Variable ratio transmission unit |
| US4304154A (en) * | 1978-09-05 | 1981-12-08 | Gkn Group Services Limited | Variable ratio transmission mechanism |
| DE2965662D1 (en) * | 1978-09-05 | 1983-07-21 | Gkn Group Services Ltd | Variable ratio transmission mechanism |
| US4819494A (en) * | 1987-04-01 | 1989-04-11 | Giuliani Robert L | Continuously variable transmission |
| DE4012060A1 (en) * | 1989-04-19 | 1990-10-25 | Takashi Takahashi | CONTINUOUS VARIABLE GEARBOX |
| FR2675875A1 (en) * | 1991-01-18 | 1992-10-30 | Ching Shiang Huang | Variable-speed transmission mechanism |
| WO1992022759A1 (en) * | 1991-06-13 | 1992-12-23 | Dong Hwi Lee | Rotary to stepless motion converter |
| US5472388A (en) * | 1991-12-19 | 1995-12-05 | Lee; Dong H. | Rotary to stepless motion converter |
| FR2776736A1 (en) * | 1998-03-24 | 1999-10-01 | Thomson Csf | Variable speed friction drive for alternator driven by aircraft engine turbine |
| RU2004107886A (en) * | 2004-03-18 | 2005-10-10 | Ким Дмитриевич Макин (RU) | DRIVE DRIVE VARIATOR |
| WO2021024177A1 (en) * | 2019-08-05 | 2021-02-11 | Johannes Jacobus Naude | Continuously variable transmission with variable disk traction drive |
| CN212584206U (en) * | 2020-06-19 | 2021-02-23 | 李哲南 | Stepless speed variator |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US5135442A (en) | Gear arrangement for transmitting torque through an angle | |
| CN102248540B (en) | Robot driving joint | |
| DE3837541C2 (en) | ||
| CN113309833A (en) | Engaged stepless speed change mechanism | |
| US20050028627A1 (en) | Gear reduction unit | |
| CN206344170U (en) | Steering wheel and robot | |
| CN103836121A (en) | Planetary differential ring speed reducer | |
| CN1888473A (en) | Single inputting and double outputting planetary speed reducer | |
| US4671134A (en) | Automatic transmission for motorcycles | |
| RU2629620C2 (en) | Single-step reduction gearbox with large ratio for aircraft engine | |
| US5896775A (en) | Gear arrangement | |
| EP0765444B1 (en) | Gear reducer comprising eccentrics | |
| CN203836119U (en) | Jiawu differential mechanism | |
| CN207539285U (en) | Transmission device, the stereo garage including the transmission device and the vehicles | |
| CN2221123Y (en) | Dual-ring speed reducer | |
| CN2200727Y (en) | Double transmission shifting speed reducer | |
| CN1048441A (en) | Planetary transmission of circular arc gear engaged with pin gear | |
| CN2056469U (en) | Planetary gear type reduction device | |
| CN202360685U (en) | Power system and planetary gear assembly thereof | |
| CN216343768U (en) | Real-time torque differential mechanism | |
| CN202220832U (en) | Involute gear transmission device with few teeth and perpendicularly intersected axes | |
| CN219119750U (en) | Staggered-layer-arrangement type four-stage gear transmission | |
| CN216112029U (en) | Face gear and gear box comprising same | |
| CN218582171U (en) | Transmission device | |
| CN85203495U (en) | Wobbled involute face-gear drive |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination |